Transmission



July 21, 1964 W. B. HERNDON ETAL TRANSMISSION 3 Sheets-Sheet 1 OriginalFiled Sept. 16, 1960 MMV S T m m i ATTOR/VY July 21, 1964 w. a. HERNDONETAL 3,141,354

TRANSMISSION Original Filed Sept. 16, 1960 3 Sheets-Sheet 2 IN VEN TORSATYURNEY July 2l, 1954 w. a. HERNDON x-:TAL 1 3,141,354

TRANSMISSION Original Filed Sept. 16, 1960 5 Sheets-Sheet 3 IN VEN TORSUnited States Patent O 3,141,354 TRANSMISSION Walter B. Herndon, AnnArbor, and Howard E. Olsen,

Plymouth, Mich., assignors to General Motors Corporation, Detroit,Mich., a corporation of Delaware `('Jontinuation of application Ser. No.56,445, Sept. 16,

1960. This application Mar. S, 1962, Ser. No. 180,922

12 Claims. (Cl. 74-677) This invention relates to transmissions, andmore particularly to an automatic transmission adapted for use in motorvehicles.

This application is a continuation of our pending patent applicationSerial No. 56,445, led September 16, 1960, now abandoned.

An object of this invention is to provide a transmission incorporatingplanetary gearing and a hydrodynamic torque transmitting member capableof accomplishing transition of drive ratio smoothly and without harshtorque reaction bumps.

Another object of this invention is to provide a transmissionincorporating two planetary gearing units and a hydrodynamic torquetransmitting member incorporating an impeller and a pair of turbineswherein the transmission power delivery shaft in one drive ratio isdriven at the torque multiplication of one gear unit and thehydrodynamic torque transmitting device, at a second drive ratio isdriven mechanically through the torque multiplication of a second gearunit only, and in a third drive ratio is driven through the hydrodynamictorque transfer unit and the second gear unit with the second gear unitlocked up for direct drive and the hydrodynamic torque transfer unitfunctioning as a fluid coupling rather than a hydraulic torqueconverter.

A further object of this invention is to provide a transmission havingtwo planetary gearing units and a hydrodynamic torque transmitting unitincorporating an impeller and two turbine members wherein one of theturbines is mechanically connected to a sun gear of one gear unit andwherein the second turbine, the planet carriers of each gear unit andthe power delivery shaft are all connected together for rotation as aunit.

An additional object of this invention is to provide in a transmissionof the class described a housing having a pair of support webs havingaxially extending support members thereon wherein the power input shaftis supported for rotation both within and on the external surface of oneof the support members, wherein a brake sleeve shaft fixed to a sun gearof one planetary unit is supported for rotation in the other of saidsupport members, wherein a hollow sleeve shaft fixed to one turbine of ahydrodynamic torque transmitting unit and to the planet carriers offirst and second gear units extends through and is rotatably supportedin the brake sleeve shaft, and wherein an additional shaft driven byanother turbine and fixed to a sun gear of a second planetary gearingunit extends through the aforementioned hollow sleeve shaft and ispiloted at one end in an engine driven power input shaft and at theother end in the final power delivery shaft.

A further object of this invention is to provide in a transmissionhaving a sun gear carried by a shaft and having spline teeth on theshaft and gear capable of limited angular rotation with respect to eachother, an anti-rattle device capable of maintaining the spline teeth outof physical Contact with each other through a predetermined angularrotation of the spline teeth with respect to each other.

Another object of this invention is to provide in a transmission animpeller and a rst turbine having blades thereon disposed axially in thedirection of the transmission main shaft and perpendicular to the planeof rota- 3,141,354 Patented July 21, 1964 ICC tion thereof wherein theblades of the turbine and impeller are recessed in the inner portion ofthe parting zone thereof to receive a second turbine and wherein theblades of the second turbine are disposed at an angle to the plane ofrotation thereof and are provided with a lip portion extending parallelto the blades of the impeller and first turbine.

These and other objects of this invention will be apparent from thefollowing description and claims taken in conjunction with the followingdrawings, in which:

FIGURE 1 is a sectional view through a transmission constructed inaccordance with the principles of this invention.

FIGURE 2 is a sectional view through a hub for one of the turbines ofthe transmission.

FIGURE 3 is a top plan view of the hub shown in FIGURE 2 illustratingthe blade receiving slots in the hub.

FIGURE 4 is an enlarged sectional view of the slot shown in FIGURE 3,taken along the line 4-4 of FIG- URE 3.

FIGURE 5 is a side elevation of one of the blades of one of the turbinesadapted to be carried by the hub illustrated in FIGURES 2 through 4.

FIGURE 6 is a top plan view of the blade shown in FIGURE 5.

FIGURE 7 is an enlarged view taken along the line 7-7 of FIGURE 6.

FIGURE 8 is a sectional view through one of the sun gears of thetransmission taken along the line 8 8 of FIGURE 9.

FIGURE 9 is an end View of the sun gear shown in FIGURE 8.

FIGURE 10 is a sectional View of an anti-rattle or damper device takenalong the line 10--10 of FIGURE 11 and adapted for use in connectionwith the sun gear shown in FIGURES 8 and 9.

FIGURE 11 is an end view of the damper device shown in FIGURE 10.

FIGURE 12 is a partially sectional View through a shaft adapted toreceive the sun gear shown in FIGURES 8 and 9 and the anti-rattle deviceshown in FIGURES 10 and 11.

FIGURE 13 is a sectional view taken along the line 13-13 of FIGURE 12.

Referring to FIGURE 1 there is shown a transmission 10 having an outercase 11, a hydrodynamic torque transmitting unit 12, a rst gear unit 13and a second gear unit 14.

An engine driven flywheel 1 is connected to drive a power input shaft 3by means of a vibration dampener 2. A gear 4 on flywheel 1 may beengaged by an engine starter, not shown, to start the vehicle engine. Acasing web 5 extends radially inwardly and carries an axially extendingannular support boss 6. A pump 7 driven by shaft 3 delivers oil underpressure to a channel 8 in boss 6 when shaft 3 is driven by the engine,not shown. Shaft 3 extends through boss 6 and is shaped at one end toprovide an axially extending annular ange support 9 overlying theexterior surface of boss 6 and adapted to receive a torus cover 15. Boss6 on web 5 therefore supports power input shaft 3 both internally andexternally of the boss and rotatably supports torus cover 15. A pumpcover 16 bolted to web 5 carries an oil seal 17 and also providessupport for input shaft 3. A bushing 18 is disposed between shaft 3,boss 6 and a pump port plate 19 for support purposes. A torus coverinsert ring 20 rides on the external surface of boss 6 and rotates withtorus cover 15. A roller bearing assembly 21 is disposed between web 5and the end of the torus cover 15 to absorb thrust. Torus cover 15 isdriven by shaft 3 at engine speed and carries a series of dump valves22,

one of which is shown. Fluid pressure may be admitted to a chamber 23 tocause valve 22 to block olf an exhaust port 24 to prevent exhaust of uidfrom the interior of cover 15. If chamber 23 is connected to exhaust, aspring 25 and centrifugal force will cause valve 22 to connect chamber26 to exhaust, through exhaust port 24.

A driving torus or impeller 30 having a series of vanes 31 and a clutchdrum 32 is bolted to torus cover 15 for rotation therewith. Varies 31 inclutch drum 32 are cast integrally with driving torus 30. A driven torusassembly or turbine 33 is composed of a semi-torus shell 34, a series ofvanes 35 and a hub 36. Vanes 35 are provided with tabs 37 and 38 whichmay be inserted through suitable slots (not shown) in shell 34 androlled over on the outer surface of the shell. A support ring 39supports vanes 35 at the open edge of the vanes. Varies 35 may also bebrazed to shell 34 to form a unitary assembly of the vanes and shell.Shell 34 is brazed to a hub 36.- A thrust race 40 carried by hub 36cooperates with a roller bearing 41 disposed between race 40 and the endof shaft 3 to absorb thrust. Hub 36 is splined to a transmission mainshaft 42 supported for rotation in power input shaft 3 by a bushing 43.It will be noted that the vanes 31 and 35 are shaped to provide outerand innerparting Zones indicated at 44 and 45. In the outer parting zone44 the edges of the vanes 31 are disposed closely adjacent to the edgesof vanes 35. In the inner parting zone-45, the edges of vanes 31 and 35are recessed to provide an open space adapted to receive a Secondturbine 46. Vanes 31 and 35 are at metal vanes which extend axially inthe dirction of transmission main shaft 42 and perpendicular to theplane of rotation of the torus cover and drive torus 30. Turbine 46 iscomposed of an assembly of blades 47 and a hub 43 having an axiallyextending support boss 49 thereon;

A first gear unit 13 is composed of a sun gear 50, planet carrier 51, aring gear 52 and a plurality of planet gears 53 in mesh with sun gear 50and ring gear 52. A hollow sleeve shaft 54 formed integrally as part ofplanet carrier 51 is splined to hub 48. Second gear unit 14 is composedof a sun gear 55, a ring gear 56,v planet carrier 57 l and a pluralityof planet gears 53. A series of clutch discs 60 are axially slidable onring gear 56 and rotatable with the ring gear. A series of clutch discs59 are axially slidable on clutch drum 32 and are driven by the clutchdrum. The drive and driven clutch discs comprise an engageable andreleasable clutch indicated generally at 61. Sun gear 55 is providedwith a hollow sleeve extension 62. A brake drum 63 formed integrallywith ring lgear 52 is splined to sleeve shaft 62 so that ring gear 52and sun gear 55 rotate as a unit. A brake 64 may be applied to drum 63to prevent rotation of ring gear 52 and sun gear 55. Brake 64 may beapplied to drum 63 in any suitable manner as, for example, a fluidpressure operated servo operating through suitable linkage, not shown. Arotatable cylinder 65 bolted to an extension 66 of ring gear 56 has aclutch actuating piston 67 disposed therein adapted to engage clutch 61when fluid pressure is admitted to a chamber 63. A clutch'release spring69 seated upon extension 66 and piston 67 assures complete release ofclutch 61 upon release of fluid pressure from chamber 68. A conicalbrake member '70 is splined to cylinder 65 for axial motion with respectto cylinder 65 and is rotatable therewith. A cylinder 71 xed to housing11 contains a piston 72 pinned to the cylinder for axial motion and toprevent rotation of the piston by means of a pin 73. Piston 72 iseffective to force brake member 70 against a conical backing member xedto housing 11 to prevent rotation of ring gear 56 when fluid pressure isadmitted to a chamber 74. An axially extending hollow support boss 75 oncylinder 71 supports ring gear 56 and cylinder 65. A brake releasespring 76 seated upon a spring seat 77 carried by boss 75 ,and uponpiston 72 assures complete release ofthe pis,-

4 ton from brake 70 upon release of fluid pressure from chamber 74.

VA roller bearing 80 is disposed between one edge of hub 36 and a thrustrace 81 which bears against one end of sleeve shaft 54 and against hub48. Hub 43 is supported at one side on hub 36 and on the opposite sidewith the portion 49 supported on the axial extension 82 of planetcarrier 57. Torus member 30 is rotatably supported upon extension 49 ofhub 48 by means of a bushing 33. Since turbine hub 48 and carrier 57 areeach splined to shaft 54, the turbine 46, carrier 57 and carrier 51 allrotate as a unit. Planet carrier 51 is connected to an upstanding flange85 on powerdelivery shaft S7 by means of a pin S4 for rotation therewithas a unit. A gear 86 on flange 85 may receive a parking brake pawl orratchet, not shown, to lock Vshaft 87 against rotation when thetransmission is conditioned for Parle Sleeve shaft 62 is supported forrotation on shaft 54 by spaced bushings S3 and S9, and is supported onboss '75 of casing web 71 by means of bushings 90 and 91. A bushing 92supports brake drum 63 on planet carrier 51. Shaft 42 is piloted in oneend of output shaft 37 by means of a bushing 93. Shaft S7 is rotatablysupported in housing 11 by a roller bearing 94. Y

As heretofore stated, the vanes 31 and 35 of impeller 30 and turbine 33are straight vanes disposed in the assembly perpendicular to their planeof rotation and eX- tending axially in the direction of main shaft 42.As shown in FIGURES 2 through 4, hub 48 carries a series of splines 95adapted to cooperate with splines on sleeve shaft 54 of FIGURE 1.Portion 49 is recessed to receive an oil seal ring 97 shown in FIGURE 1.A series of slots 98 shown in FIGURE 3, are provided to receive the baseof vanes 47. Slots 93 are cut in hub 48 at an angle of 34 to the planeof rotation of the hub and to the axis of rotation of the hub.v As shownin FIGURE 3, the angle of slots 98 is 34 degrees to the axis of rotationof the hub. Slots 98 each have substantially parallel side walls 99 and.100 extending inwardly from the outer extremity of the slot, part-wayinwardly toward the base of the slot. Side walls 99 and 100 are cut backor recessed in the portion thereof adjacent the base of the slot asindicated at 101 and 102 to form a dovetail adapted to receive the baseof blade 47.

As shown in FIGURES 5 through 7, vane 47 includes a base portion 105 andan upstanding blade portion 106 having a lip 107 bent at an angle tostraight blade portion 106. Slot 98 of hub 48 is cut at an angle of 34degrees as stated. Lip 107 of vane 47 is bent at an angle of 34 degreesto the plane containing the main straight blade portion 106 asparticularly shown in FIGURE 6. In the assembly of the vane 47 to thehub, the Vane p0rtion 106 therefore lies at'an angle of 34 degrees tothe plane of rotation of the hub, while lip 107 extending outwardlybeyond the edge of the hub extends parallel t0 the vanes 35 of turbine34. As shown in FIGURE 7, the base 105 of vane 47 includes substantiallyparallel side wall portions 109 and 110 and outwardly diverging wallportions 111 and 112 adapted to be received by the portions 99-100 and101-102 of hub 48. An annular support ring 114 shown in FIGURE 1 litsover the outer edge of the blade assembly into contact with anupstanding lip 113 formed on the vanes.

In the assembly of sun gear 50 to transmission mainshaft 42, sun gear 50is splined to the mainshaft. As shown in FIGURE 8 twelve splines 115 areprovided on the internal surface of the gear. A slot 116 shownparticularly in FIGURES 8 and 9 is cut in the gear hub side wall, theslotbeing located on the center of a spline tooth as shown. 'Ihe splinesformed on gear 50 comprise.12 teeth, 10 diametral pitch, 27 pressureangle, 1.0692 base circle diameter. The minimum effective space widthallowable is .1932 while the maximum effective allowable space width is.1953. The minimum dimension for space width is .1945 while the maximumallowable dimension for spacewidth is .1955. Referring Ito FIGURES 12and 13 which show the splines 117 0n transmission shaft 42 adapted toreceive the sun gear splines 115, the number of teeth, diametral pitch,pressure angle and base circle diameter are the same as those of thesplines on gear 50. The minimum effective tooth -thickness is .1198,maximum effective tooth thickness is .1225, minimum dimension, tooththickness .1193 and maximum allowable tooth thickness .1215. It will beapparent that with the sun gear assembled on shaft 42, the sun gearsplines 115 and shaft splines 117 will mate loosely due to manufacuringtolerances. It has been found that, particularly when operating insecond gear drive with the hydrodynamic torque transmitting deviceemptied of working fluid, a rattle occurs in gear unit 13 due to theplay between these splines. In order to minimize this rattle, aresilient damper 120 shown particularly in FIGURES l and 11 is assembledto sun gear Si). Damper 121) is made up of an assembly of an annularU-shaped metallic retainer 121 having an annular base 122 and a pair ofbent over side walls or flanges 123 and 124. An upstanding ear or tang125 is struck up from the base 122. A resilient damper 120 havingsplines 126 formed thereon is disposed within metallic retainer 121between the base 122 and side walls 123 and 124, the resilient damperbeing bonded to the metallic retainer. In the aS- sembly of theresilient damper to the retainer, the tang 125 is disposed such that thecenter of the tang is disposed on the center of one of the spline teethas particularly shown in FIGURE 11. This facilitates the assembly of thedamper to the sun gear t?. In assembling the damper to the gear,retainer 121 is press fitted to an axially extending annular boss orextension 127 on gear 511 best shown in FIGURE 8, so that the retainercannot move with respect to the gear. Tang 125' fits into slot 115 ofgear 56B so that the splines 126 align with splines 115. The resilientmember 121) contains 12 splines 126 having the same diametral pitch,pressure angle, and base circle diameter as the splines on shaft 42 andgear 5%. In the case of the splines on the resilient member 120,however, the minimum permissible effective space width is .1107, maximumeffective space width is .1132, the minimum dimension space width is.1099 and the maximum dimension space width is .1124. It will beapparent therefore, that with the gear and dampener assembly disposed onthe splines 117 of shaft 42, the resilient splines serve to tend tocenter the gear splines with respect to those of shaft 42 such that theside walls of the gear splines are spaced from the side walls of thesplines on the shaft. In the event that a load is applied to gear 511,the resilient dampener 121) will yield to permit the side walls ofsplines 115 to contact the side walls of splines 117 so that the shaftdrives the gear. In the event no load is applied to gear 50, theresilient dampener serves to space the side walls of the metal splineson the gear and shaft from each other to prevent rattle. The dampener isparticularly effective when operating in second gear to prevent rattle.The tang 125 and slot 116 automatically align the splines on gear 50 andresilient member 120, thereby facilitating the mounting of the gear anddampener assembly on shaft 42. When operating in second gear, thedampener permits approximately thirty degrees of rotation of the gear 50with respect to shaft 42 in either direction before metal to metalcontact of the splines on the shaft and gear occurs. In effect, theworking pitch diameter of the dampener splines is greater than those ofshaft 42 but less than that of the splines of gear 5t), so that thedampener centers the splines of the gear out of contact with those ofthe shaft when no load is applied to the gear. When torque is applied toshaft 42, the shaft rotates through a limited angular rotation withrespect to the gear to permit the side walls of the gear splines to meshwith the side walls of the shaft splines.

Referring to FIGURE 1, the transmission, in operation, is adapted toprovide three forward drive ratios including low, second and high ordirect drive plus reverse. For low or first gear drive, hydrodynamictorque transmitting unit 12 is filled with working fluid and brake 64 isapplied to drum 63 to` prevent rotation of ring gear 52. At engine idle,with the vehicle stopped, planet carrier 51 will be held againstrotation due to the load of the vehicle on shaft 87. Driving torus 30will be driven at engine speed, but turbines 33 and 46 will remainstationary. As the torus 3) is speeded up, turbine 33 will initiallydrive sun gear 50 through transmission mainshaft 42 and cause planetcarrier 51 and shaft 87 to rotate forwardly in the reduction of gearunit 13. Turbine 46 will likewise rotate forwardly in reduction drive atthe speed of rotation of output shaft 87. In this stage of operationturbine 45 functions as a forwardly rotating reaction member tore-direct tiuid delivered by turbine 33 to the impeller blades 31 sothat the re-directed ud entering impeller 3@ will tend to rotate theimpeller forwardly. In this drive ratio the hydrodynamic torquetransmitting unit functions as a hydraulic torque converter so thatoutput shaft 87 is driven partially by mechanical torque multiplicationof gear unit 13 and partially by the torque multiplication of unit 12.

For second gear drive, unit 12 is emptied of fluid, brake 64 remainsengaged, and clutch 59-69 is engaged. Shaft S7 is driven entirelymechanically at the drive ratio of gear unit 14. For direct drive,clutch 59-60 remains engaged, and unit 3i) is re-iilled with liuid,while brake 54 is released. In direct drive, turbine 47 no longerfunctions as a torque converter reaction member, but rather functions asa second turbine.

The arrangement of the gearing, in combination with the two turbinehydrodynamic units 12 with the two turbines and the specific shaftingassembly of shafts 42, 54 and 62 provides a very compact three speedtransmission capable of hydraulic torque multiplication in low geardrive, mechanical drive in second gear, and split mechanical drive andhydraulic drive in high gear. The anti-rattle device 121i prevents gearrattle in gear unit 13 when hydraulic unit 12 is empty of working fluid.,The housing support iianges 6 and 71 provide for a rigid assembly ofthe rotating parts capable of a long and useful life. The lip 1117 onblades 106 is provided to cause the turbine 47 to act as a turbinerather than a converter reaction member at a relatively low rotatingspeed. The lip 47 will receive iiuid from turbine 35 on the rear side ofthe lip so that the working iiuid will, at a relatively low speed ofrotation of turbine 47 tend to drive member 47 forwardly in thedirection of rotation of turbine 35 rather than reversely. Thus, turbine47 only initially functions as a converter reaction member, and at arelatively low speed of rotation functions as a second fluid couplingturbine member.

Blades 4-7 of turbine 46 are disposed in the recess 45 between blades 31and 35 at the inner radial Zone of fluid liow and extend across theparting zone 44 wherein the edges of blades 31 and 35 are disposedclosely adjacent to each other. By placing the blades 47 in the innerradial zone as shown and providing lip 1137 thereon extending axiallyand parallel to blades 35 into close yproximity to the blades 45,turbine 46 functions as a converter reaction member only at low rotativespeeds and quickly receives fluid on the rear surface of lip 197 andblades 47 to change its function to that of an impeller. This provideshydrodynamic torque multiplication for start, but improves efiiciencywhen operating in direct drive.

We claim:

1. In a transmission, a hydrodynamic torque transmitting device and rstand second planetary gearing units, said hydrodynamic torquetransmitting device including an engine driven impeller and first andsecond turbine members, said planetary gearing units each including a t2? planet carrier supporting a plurality of planet pinion gears in meshwith a ring gear and a sun gear, means connecting said first turbine tothe sun gear of said first gear unit for driving the same, meansconnecting said second turbine to the planet carriers of both of saidgear units for rotation therewith as a unit, an engageable andreleasable brake effective when engaged to prevent rotation of the ringgear of said rst gear unit and the sun gear of said second gear unit,and an engageable and releasable clutch effective when engaged toconnect the ring gear of said second gear unit to said engine.

2. In a transmission, a hydrodynamic torque transmitting device of thetype adapted to be alternately filled with and emptied of working fluid,said torque transmitting device including an engine driven impeller andrst and second turbines, first and second planetary gearing units eachincluding a planet carrier supporting a plurality of planet pinion gearsin mesh with a ring gear and a sun gear, means connecting said firstgear unit sun gear to said first turbine for rotation therewith, meansconnecting said second turbine to both of said planet carriers forrotation therewith as a unit, a final power delivery shaft connected forrotation with the planet carriers and second turbine, means connectingthe ring gear of said first gear unit to the sun gear of said secondgear unit for rotation therewith, an engageable and releasable brakeeffective when engaged and said hydrodynamic torque transmitting unit isfilled with working fluid to prevent rotation of said first gear unitring gear to establish lowgear drive through said first gear unit, anengageable and releasable clutch for clutching the ring gear of saidsecond gear unit to said engine, said brake and said clutch beingengaged and said hydrodynamic torque transmitting unit being emptied ofworking fluid to establish second gear drive through said transmission,said brake being released, said clutch engaged and said hydrodynamictorque transmitting unit filled with fluid to establish direct drivethrough said transmission.

3. In a transmission, a transmission housing, first and second supportwebs on said housing, each web having a hollow axially extending supportfiange formed thereon at the inner end thereof, an engine driven powerinput shaft extending through said first iange and rotatably supportedtherein, an axially extending drive member on said power input shaft andsupported for rotation on the outer surface of said first fiange, ahydrodynamic torque transmitting unit including an impeller driven bysaid power input shaft and first and second turbines, a final powerdelivery shaft supported for rotation in said housing, first and secondplanetary gearing units, each of said gear units including a planetcarrier supporting a plurality of planet pinion gears in mesh with a sungear and a ring gear, a first hollow sleeve shaft supported for rotationin said second support fiange and connecting said first gear unit ringgear to said second gear unit sun gear for rotation therewith, anengageable and releasable brake effective when engaged to preventrotation of said first hollow sleeve shaft, a second hollow sleeve shaftsupported for rotation in said first hollow sleeve shaft,

said second hollow sleeve shaft connecting said second turbine, both ofsaid planet carriers and said final power delivery shaft to each otherfor rotation as a unit, a third hollow sleeve shaft extending throughsaid second hollow sleeve shaft and piloted in said engine driven powerinput shaft and said final power delivery shaft, said third hollowsleeve shaft connecting said first turbine to said first gear unit sungear for rotation therewith as a unit, and an engageable and releasableclutch effective when engaged to connect the ring gear of said secondgear unit for rotation with said engine driven power input shaft.

4A In a transmission, a hydrodynamic torque transmitting deviceincluding an engine driven impeller and first and second turbines, saidimpeller and said first turbine each having blades extendingperpendicular to their plane of rotation and facing each other in closeproximity at an outer parting Zone, said blades being recessed inwardlyof said outer parting zone to receive said second bladed turbine, saidsecond turbine having blades extending across the inner limit of saidouter parting zone, first and second planetary gearing units each havinga planet carrier supporting a planet pinion gear in mesh with a ringgear and a sun gear, a drive connection connecting said rst turbine tosaid first gear unit sun gear for driving said sun gear, a driveconnection connecting said second turbine to both of said planetcarriers for rotation therewith as a unit, a final power delivery shaftdriven by said first gear unit planet carrier, means connecting saidfirst gear unit ring gear to said second gear unit sun gear for rotationtherewith as a unit, a selectively engageable and releasable brakeeffective when engaged to prevent rotation of said first gear unit ringgear and said second gear unit sun gear, and an engageable and releaableclutch effective when engaged to connect said second gear unit ring gearfor rotation with said engine driven power input shaft.

5. In a transmission, a hydrodynamic torque transmitting deviceincluding an engine driven impeller and first and second turbines, saidimpeller and said rst turbine each having blades extending perpendicularto their plane of rotation and facing each other in close proximity atan outer parting zone, said blades being recessed inwardly of said outerparting zone to receive a second bladed turbine, said second turbinehaving blades extending across said recess and disposed at an angle totheir plane of rotation to receive fluid from said first turbine andredirect said fluid into said impeller, the blades of said secondturbine each having a lip thereon extending perpendicular yto the planeof rotation of said second turbine, first and second planetary gearingunits each having a planet carrier supporting a planet gear in mesh witha ring gear and a sun gear, means connecting said first turbine to thesun gear of said first gear unit to drive the same, a final powerdelivery shaft, means connecting said second turbine, both of saidplanet carriers and said final power delivery shaft to each other forrotation as a unit, means connecting the ring gear of said first gearunit to the sun gear of said second gear unit for rotation therewith asa unit, a selectively engageable brake effective when engaged to preventrotation of said first gear unit ring gear and said second gear unit sungear, and an engageable and releasable clutch effective when engaged toconnect said second gear unit ring gear to said engine driven impellerfor rotation therewith.

6. In a transmission, a hydrodynamic torque transmitting device of thetype adapted to be alternately filled with and emptied of working fluid,said device including an engine driven impeller and first and secondturbines, said impeller and said first turbine each having bladesextending perpendicular to their plane of rotation and facing each otherin close proximity at an outer parting zone, said blades being recessedinwardly of said outer parting zone to receive said second turbine, theblades of said second turbine extending across the inner limit of saidouter parting zone and having a lip thereon extending perpendicular totheir plane of rotation into close proximity to the blades of said firstturbine, first and second planetary gearing units each having a planetcarrier supporting a planet gear in mesh with a sun gear and Y a ringgear, means connecting said first turbine to said first gear unit sungear for rotation therewith, a final power delivery shaft, meansconnecting said second turbine to both of said planet carriers and saidfinal power delivery shaft for rotation therewith as a unit, meansconnecting said first gear unit ring gear to said second gear unit sungear for rotation therewith as a unit, an engageable and releasablebrake adapted to be engaged to prevent rotation of said first gear unitring gear to establish reduction drive through said first gear unit andsaid hydrodynamic torque transmitting device when said hydrodynamictorque transmitting device is filled with fiuid, an engageable andreleasable clutch effective when engaged to connect said second gearunit ring gear for rotation with said impeller, said brake and clutchbeing engaged and said hydrodynamic torque transmitting device beingemptied of fluid to establish second gear drive through said second gearunit, said brake being released, said clutch engaged, and saidhydrodynamic torque transmitting device filled with fiuid to establishdirect drive through said transmission.

7. In a transmission, a hydrodynamic torque transmitting device of thetype adapted to be alternately filled with and emptied of working fluid,said device including an engine driven impeller and first and secondturbines, first and second planetary gearing units each having a planetcarrier supporting a pinion gear in mesh with a ring gear and a sungear, a shaft driven by said first turbine having a set of splinesthereon adapted to receive splines on said first gear unit sun gear,said shaft being rotatable through a limited angular rotation withrespect to said sun gear before driving the same, an anti-rattle devicefor preventing rattle of said splines comprising a resilient memberfixed to said sun gear and having splines thereon closely mating withthe splines of said shaft, said resilient member being normallyeffective to dispose said sun gear on said shaft with the splines ofsaid sun gear out of physical contact with the splines on said shaftwhen said hydrodynamic torque transmitting member is emptied of fiuid, afinal power delivery shaft, means connecting said second turbine, bothof said planet carriers and said final power delivery shaft to eachother for rotation as a unit, means connecting the ring gear of saidfirst gear unit to the sun gear of said second gear unit for rotationtherewith, an engageable and releasable brake effective when engaged toprevent rotation of said first gear unit ring gear and said second gearunit sun gear, and an engageable and releasable clutch effective whenengaged to clutch said second gear unit ring gear to said impeller.

8. In a transmission, a hydrodynamic torque transmitting device of thetype adapted to be alternately filled with and emptied of working fluid,said device including an engine driven impeller and first and secondturbines, first and second planetary gearing units each having a planetcarrier supporting a pinion gear in mesh with a ring gear and a sungear, a shaft driven by said first turbine having a set of splinesthereon adapted to receive splines on said first gear unit sun gear,said shaft being rotatable through a limited angular rotation withrespect to said sun gear before driving the same, an anti-rattle devicefor preventing rattle of said splines comprising a resilient memberfixed to said sun gear and having splines thereon closely mating withthe splines of said shaft, said resilient member being normallyeffective to dispose said sun gear on said shaft with the splines ofsaid sun gear out of physical contact with the splines on said shaftwhen said hydrodynamic torque transmitting member is emptied of fiuid, afinal power delivery shaft, means connecting said second turbine, bothof said planet carriers and said final power delivery shaft to eachother for rotation as a unit, means connecting the ring gear of saidfirst gear unit to the sun gear of said second gear unit for rotationtherewith, an engageaole and releasable brake effective when engaged toprevent rotation of said first gear unit ring gear and said second gearunit sun gear, and an engageable and releasable clutch effective whenengaged to clutch said second gear unit ring gear to said impeller, saidbrake being effective when engaged to establish reduction drive throughsaid first gear unit and said hydrodynamic torque transmitting devicewhen said torque transmitting device is filled with fluid, said brakeand said clutch being simultaneously engaged to establish second geardrive through said second gear unit when said hydrodynamic torquetransmitting device is emptied of working fluid, and said brake beingreleased, said clutch engaged and said hydrodynamic torque transmittingdevice being filled with fluid to establish direct drive through saidtransmission.

9. In a transmission, a hydrodynamic torque transmitting device of thetype adapted to be alternately filled with and emptied of working fluid,said device including an engine driven impeller and first and secondturbines, said impeller and said first turbine each having bladesextending perpendicular to their plane of rotation and terminating inclose proximity to each other at an outer parting zone, the blades ofsaid impeller being recessed inwardly of said outer parting zone toreceive the blades of said second turbine, the blades of said secondturbine extending across the inner end of said parting zone at an angleto their plane of rotation and having a lip formed thereon extendingperpendicular to the plane of rotation of said blades and disposed inclose proximity to the blades of said first turbine, first and secondplanetary gearing units each having a planet carrier supporting a piniongear in mesh with a ring gear and a sun gear, a shaft driven by saidfirst turbine having a set of splines thereon adapted to receive splinesformed on said first gear unit sun gear, said shaft being rotatablethrough a limited angular rotation with respect to said sun gear beforedriving the same, an anti-rattle device for preventing rattle of saidsplines comprising a resilient member fixed to said first gear unit sungear and having splines thereon closely mating with the splines on saidshaft, said resilient member being normally effective to maintain thesplines on said sun gear and said shaft out of physical contact witheach other when said hydrodynamic torque transmitting device is emptiedof fluid, a final power delivery shaft, a hollow sleeve shaft throughwhich said splined shaft extends for connecting said second turbine andboth of said planet carriers to said final power delivery shaft, anadditional hollow sleeve shaft through which said first-mentoined hollowsleeve shaft extends for connecting the ring gear of said first gearunit to the sun gear of said second gear unit, an engageable andreleasable brake effective when engaged to prevent rotation of firstgear unit ring gear and said second gear unit sun gear, saidtransmission being effective to drive said final power output shaft inreduction drive of said hydrodynamic torque transmitting device and saidfirst gear unit when said brake is applied and said hydrodynamic deviceis filled with fluid, an engageable and releasable clutch effective whenengaged to clutch the ring gear of said second gear unit to saidimpeller for rotation therewith, said clutch and said brake beingsimultaneously engaged and said hydrodynamic device emptied of fluid toestablish second gear drive through said second gear unit, said clutchbeing engaged, said brake released and said hydrodynamic device beingiilled with fiuid to establish direct drive of said final power deliveryshaft.

l0. In a torque transmitting assembly, a first rotatable membercomprising a shaft, a second rotatable member comprising a gearsupported on said shaft for limited angular rotation with respect tosaid shaft, a set of splines on each of said members effective whenengaged to transmit torque therebetween, the splines of said rotatablemembers permitting limited angular rotation of said members with respectto each other from a first position wherein said splines are in spacedrelation with respect to each other to a second position wherein saidsplines are engaged, said assembly at times being subjected to a loadand at times being operated Without loading, means for rotating saidrotatable members to said first position when said device is operated inthe absence of load to prevent rattle of said splines and for permittingangular rotation of said rotatable members to said second position fortransmission of torque through said splines when said assembly issubjected Ito load, said means comprising an annular ring formed ofresilient material, said ring having a body fixed for rotation with saidgear and a set of splines formed on said resilient body, splines on saidshaft in close mating relationship with said resilient splines on saidresilient body, the splines on said resilient body being axially spacedfrom the splines on said gear.

11. 1n a torque transmitting assembly, a shaft having splines thereon, agear having splines thereon intermeshing With the splines of said shaft,said gear and said shaft being capable of limited angular rotation Withrespect to each other from a first position wherein said splines arespaced from each other when said assembly is operated in the absence ofload to a second position wherein said splines are in contact totransmit torque When said assembly is operated under load, means forpositioning said gear and said shaft in said iirst position to preventrattle of said splines When said assembly is operated in the absence ofload, said means comprising a resilient annular member fixed to saidgear for rotation therewith and having a set of splines formed thereonand in close mating relationship with splines on said shaft, the splineson said resilient member being disposed axially at one side of thesplines of said gear.

12. In a torque transmitting assembly, a shaft having splines thereon, agear having splines thereon in intermeshing relationship with thesplines of said shaft, said intermeshing splines permitting limitedangular rotation of said gear and said shaft prior to contact of saidsplines, an anti-rattle device for preventing rattle of said splinescomprising an annular ring of resilient material having splines formedthereon, a metallic ring on said resilient ring, Va recess in said gearadapted to receive said antirattle device, a slot in the side Wall ofsaid gear disposed in axial alignment with one of the upstanding splinesof said gear, an upstanding flange on said metallic ring disposed inalignment with one of the upstanding splines on said resilient member,said resilient member being press iitted into the recess in said gearwith said tang disposed in said gear slot to align the splines of saidresilient member with those of said gear, the splines of said resilientmember being in close mating relationship with the splines of said shaftwhereby said resilient member is normally `eective to dispose said gearon said shaft with the splines .of said gear and shaft in spacedrelation with respect to each other.

References Cited in the le of this patent UNITED STATES PATENTS1,297,835 Guay Mar. 18, 1919 1,636,262 Troendly July 19, 1927 2,505,120Jackson Apr. 25, 1950 2,961,856 Selzer Nov. 29, 1960 I 3,008,349Winchell et al. Nov. 14, 1961 FOREIGN PATENTS 406,934 Germany Dec. 4,1924

7. IN A TRANSMISSION, A HYDRODYNAMIC TORQUE TRANSMITTING DEVICE OF THETYPE ADAPTED TO BE ALTERNATELY FILLED WITH AND EMPTIED OF WORKING FLUID,SAID DEVICE INCLUDING AN ENGINE DRIVEN IMPELLER AND FIRST AND SECONDTURBINES, FIRST AND SECOND PLANETARY GEARING UNITS EACH HAVING A PLANETCARRIER SUPPORTING A PINION GEAR IN MESH WITH A RING GEAR AND A SUNGEAR, A SHAFT DRIVEN BY SAID FIRST TURBINE HAVING A SET OF SPLINESTHEREON ADAPTED TO RECEIVE SPLINES ON SAID FIRST GEAR UNIT SUN GEAR,SAID SHAFT BEING ROTATABLE THROUGH A LIMITED ANGULAR ROTATION WITHRESPECT TO SAID SUN GEAR BEFORE DRIVING THE SAME, AN ANTI-RATTLE DEVICEFOR PREVENTING RATTLE OF SAID SPLINES COMPRISING A RESILIENT MEMBERFIXED TO SAID SUN GEAR AND HAVING SPLINES THEREON CLOSELY MATING WITHTHE SPLINES OF SAID SHAFT, SAID RESILIENT MEMBER BEING NORMALLYEFFECTIVE TO DISPOSE SAID SUN GEAR ON SAID SHAFT WITH THE SPLINES OFSAID SUN GEAR OUT OF PHYSICAL CONTACT WITH THE SPLINES ON SAID SHAFTWHEN SAID HYDRODYNAMIC TORQUE TRANSMITTING MEMBER IS EMPTIED OF